EP2703695B1 - Kombinierter Schmierring - Google Patents

Kombinierter Schmierring Download PDF

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Publication number
EP2703695B1
EP2703695B1 EP13181284.4A EP13181284A EP2703695B1 EP 2703695 B1 EP2703695 B1 EP 2703695B1 EP 13181284 A EP13181284 A EP 13181284A EP 2703695 B1 EP2703695 B1 EP 2703695B1
Authority
EP
European Patent Office
Prior art keywords
groove
oil ring
axial direction
along
pieces
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Revoked
Application number
EP13181284.4A
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English (en)
French (fr)
Other versions
EP2703695A1 (de
Inventor
Hideshi Hitosugi
Kenji Arai
Kazutomo Takahashi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nippon Piston Ring Co Ltd
Original Assignee
Nippon Piston Ring Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Application filed by Nippon Piston Ring Co Ltd filed Critical Nippon Piston Ring Co Ltd
Publication of EP2703695A1 publication Critical patent/EP2703695A1/de
Application granted granted Critical
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Revoked legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F16J9/064—Rings with a flat annular side rail
    • F16J9/066—Spring expander from sheet metal
    • F16J9/068—Spring expander from sheet metal corrugated in the axial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F16J9/064—Rings with a flat annular side rail
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F16J9/064—Rings with a flat annular side rail
    • F16J9/066—Spring expander from sheet metal

Definitions

  • the present invention relates to a combined oil ring, and, more particularly, to a three-piece combined oil ring including a pair of upper and lower side rails and a spacer expander arranged therebetween.
  • Oil rings that have been known up to now scrape extra engine oil attached to a cylinder inner wall surface of an internal combustion engine, and form a proper oil film, to thereby prevent a piston from being seizure along with an operation of the internal combustion engine.
  • Various forms have been known for such oil rings.
  • patent application publication EP2365233A1 describes a combined oil ring according to the preamble of claim 1.
  • United States Patent Number US5195758 describes a three-piece oil control ring assembly.
  • Japanese Patent Laid-Open No. 2011-185383 describes a combined oil ring including a pair of upper and lower side rails and a spacer expander arranged therebetween.
  • the spacer expander includes: a large number of upper pieces and lower pieces that are alternately arranged in a circumferential direction so as to be spaced apart in an axial direction and the circumferential direction; coupling pieces that respectively couple the adjacent upper pieces and lower pieces; and ear parts that are each formed so as to erect in an inner circumferential end portion of each of the upper pieces and the lower pieces, and serve to push the side rails.
  • each upper piece and a lower surface of each lower piece has a groove formed thereon, and each ear part has, formed therein, a through-hole with which the groove is communicated.
  • the scraped engine oil flows out through the groove and the through-hole, and hence carbon sludge is prevented from being deposited between the spacer expander and the side rails.
  • the conventional combined oil rings still have a problem that, if the internal combustion engine is operated for a long period of time, carbon sludge is gradually deposited in these portions, and hinders the engine oil from smoothly flowing out.
  • Japanese Patent Laid-Open No. 2011-185383 does not describe specific numerical values for dimensions of the oil ring, and hence optimal dimensions and shape for solving the above-mentioned problem are required.
  • the present invention which has been made in view of the above-mentioned problem, has an object to provide a combined oil ring in which carbon sludge is not deposited between side rails and a spacer expander even if an internal combustion engine is operated for a long period of time.
  • a combined oil ring according to the present invention is configured to be fitted in an oil ring groove of a piston, and includes: a pair of upper and lower plate-like circular side rails; and a spacer expander arranged between the pair of upper and lower side rails.
  • the spacer expander includes: a large number of upper pieces and lower pieces that are alternately arranged in a circumferential direction so as to be spaced apart in an axial direction and the circumferential direction; coupling pieces that respectively couple the adjacent upper pieces and lower pieces; and ear parts that are each formed so as to erect in an inner circumferential end portion of each of the upper pieces and the lower pieces, and serve to push the side rails.
  • At least one of an upper surface of each upper piece and a lower surface of each lower piece has a groove formed thereon.
  • Each ear part has, formed therein, a through-hole with which the groove is communicated.
  • the through-hole is formed such that a distance along the axial direction between one of an upper surface and a lower surface of each ear part at a top thereof and a deepest portion of the groove is equal to or more than 0.22 mm.
  • a sectional area of the through-hole along the axial direction be set to be equal to or more than 0.10 mm 2 .
  • the spacer expander include a side rail support part that is formed in an outer circumferential end portion of each of the upper pieces and the lower pieces so as to be one step higher than the groove; and a distance along the axial direction between the side rail support part and a groove edge part of the groove be set to 0.04 to 0.20 mm.
  • a plate thickness of the spacer expander is set to 0.17 to 0.28 mm.
  • the groove be formed along a radial direction.
  • the side rail support part have, formed therein, an opening communicated with the groove; and a sectional area of the opening along the axial direction be smaller than a sectional area of the through-hole along the axial direction.
  • a ratio of: the distance along the axial direction between one of the upper surface and the lower surface of each ear part at the top thereof and the deepest portion of the groove; to the plate thickness of the spacer expander is 0.77 to 3.00.
  • the distance along the axial direction between one of the upper surface and the lower surface of each ear part at the top thereof and the deepest portion of the groove is set to be equal to or more than 0.22 mm. Accordingly, a space between the side rails and the spacer expander can be made larger, scraped engine oil can be allowed to smoothly flow out, and deposition of carbon sludge can be prevented.
  • the sectional area of the through-hole formed in each ear part, along the axial direction is set to be equal to or more than 0.10 mm 2 . Accordingly, the engine oil between the side rails and the spacer expander can be allowed to smoothly flow out to the piston side through the through-hole.
  • a step corresponding to the distance along the axial direction between the side rail support part and the groove edge part of the groove is set to 0.04 to 0.20 mm. Accordingly, the space between the side rails and the spacer expander can be made larger, the scraped engine oil can be allowed to smoothly flow out, and deposition of carbon sludge on this area can be prevented.
  • a particularly preferable range of the step is 0.12 to 0.20 mm. If the step is less than 0.04 mm, deposition of carbon sludge cannot be prevented. If the step exceeds 0.20 mm, strength of the spacer expander becomes insufficient, resulting in lower workability and a decrease in yield.
  • the plate thickness of the spacer expander is set to 0.17 to 0.28 mm. Accordingly, the distance to the deepest portion of the groove and the sectional area of the through-hole defined above can be secured.
  • a particularly preferable range of the plate thickness is 0.20 to 0.25 mm.
  • the groove is formed along the radial direction. Accordingly, the engine oil smoothly flows out from an outer circumferential side to an inner circumferential side, whereby deposition of carbon sludge can be prevented.
  • the side rail support part has, formed therein, the opening communicated with the groove, and the sectional area of the opening is set to be smaller than the sectional area of the through-hole. Accordingly, the engine oil more smoothly flows out from the outer circumferential side to the inner circumferential side, whereby deposition of carbon sludge can be prevented.
  • the ratio of: the distance along the axial direction between one of the upper surface and the lower surface of each ear part at the top thereof and the deepest portion of the groove; to the plate thickness of the spacer expander is set to be 0.77 to 3.00. Accordingly, deposition of carbon sludge can be sufficiently suppressed.
  • a particularly preferable range of the ratio is 1.00 to 2.50. If the ratio is less than 0.77, the area of the through-hole cannot be sufficiently secured, and the suppression of the deposition of carbon sludge becomes difficult. If the ratio exceeds 3.00, the strength of the spacer expander becomes insufficient, resulting in lower workability and a decrease in yield.
  • FIG. 1 is a sectional view illustrating a main part of an internal combustion engine in which a combined oil ring according to the embodiment of the present invention is assembled, which is taken at a top of an ear part in a cylinder axial direction of the internal combustion engine.
  • FIG. 2 is a perspective view illustrating part of a spacer expander used for the combined oil ring according to the embodiment of the present invention.
  • FIG. 3 is a front view illustrating part of the spacer expander used for the combined oil ring according to the embodiment of the present invention, which is observed from an outside in a radial direction of the oil ring.
  • FIG. 4A is a perspective view illustrating part of the combined oil ring according to the embodiment of the present invention
  • FIG. 4B is a sectional view taken along a line IV-IV in FIG. 4A .
  • a combined oil ring 10 is assembled in an oil ring groove 3 formed on an outer circumferential surface of a piston 2 of the internal combustion engine so as to be in sliding contact with an inner wall of the cylinder 1, and the combined oil ring 10 thus scrapes extra engine oil attached to the inner wall of the cylinder 1, to thereby form a proper oil film on the inner wall of the cylinder 1.
  • the combined oil ring 10 includes a pair of upper and lower side rails 11, 11 and a spacer expander 12 arranged between the pair of upper and lower side rails 11, 11.
  • the side rails 11, 11 and the spacer expander 12 are made of steel or the like, and each side rail 11 is configured as a plate-like circular ring including an gap (not illustrated).
  • the spacer expander 12 is formed by plasticity processing of a steel material, and has a concavo-convex shape (corrugated shape) along an axial direction as well as a substantially circular shape along a circumferential direction.
  • This concavo-convex shape in the axial direction defines upper pieces 13 and lower pieces 14 in an end portion in the axial direction.
  • the spacer expander 12 includes a large number of the upper pieces 13 and the lower pieces 14 that are alternately arranged in the circumferential direction so as to be spaced apart in the axial direction and the circumferential direction.
  • Coupling pieces 15 respectively couple the adjacent upper pieces 13 and lower pieces 14.
  • ear parts 16 are each formed so as to erect in an arch-like shape in an inner circumferential end portion of each of the upper pieces 13 and the lower pieces 14 of the spacer expander 12, and the ear parts 16 respectively push the side rails 11, 11 to an outer circumferential side.
  • a through-hole 18 is formed along a radial direction in each ear part 16.
  • a groove 17 is formed along the radial direction on each of an upper surface 13a of the upper piece 13 and a lower surface (not illustrated) of the lower piece 14.
  • a sectional shape of the groove 17 along the axial direction is a V shape or an R shape.
  • the V shape herein includes not only a shape having adjacent oblique surfaces that intersect with each other at a sharp angle, but also a shape having adjacent oblique surfaces that are continuous with each other while describing a circular arc as illustrated in FIG. 4B .
  • a side rail support part 19 is formed in an outer circumferential end portion of each of the upper pieces 13 and the lower pieces 14 of the spacer expander 12 so as to be one step higher than groove edge parts 17a of the groove 17.
  • an opening 20 is formed in the side rail support part 19 so as to be communicated with the groove 17, and a sectional area of the opening 20 along the axial direction is set to be smaller than a sectional area of the through-hole 18 formed in the ear part 16, along the axial direction.
  • a distance A along the axial direction between a lower surface 16b (or an upper surface) of the ear part at the top thereof and a deepest portion of the groove 17 is set to be equal to or more than 0.22 mm.
  • a step B corresponding to a distance along the axial direction between an upper surface (or a lower surface) of the side rail support part 19 and the groove edge part 17a of the groove 17 is set to 0.04 to 0.20 mm and, preferably, to 0.12 to 0.20 mm. Because the step B is formed at as large a size as described above, as illustrated in FIG. 4A , when the engine oil flows to the inner circumferential side along a flow path indicated by arrows (1) extending in a corner part in which the side rail 11 and the spacer expander 12 are in contact with each other, a flow rate of the engine oil that flows in a flow path indicated by arrows (2) extending toward the groove 17 can be secured at a given value or more. Hence, carbon sludge can be prevented from being deposited in the ear part 16.
  • the sectional shape of the groove 17 along the axial direction is a V shape, the engine oil can flow more easily in the flow path indicated by the arrows (2).
  • the sectional area of the through-hole 18 formed in the ear part 16, along the axial direction, is set to be equal to or more than 0.10 mm 2 .
  • a plate thickness T of the steel material for forming the spacer expander 12 be set to 0.17 to 0.28 mm.
  • the use of the plate material having such a small thickness enables satisfactory settings of the distance A to the deepest portion of the groove 17, the step B, and the sectional area of the through-hole 18.
  • a ratio A/T of: the distance A along the axial direction between the lower surface 16b (or the upper surface) of the ear part at the top thereof and the deepest portion of the groove 17; to the plate thickness T of the steel material for forming the spacer expander 12 be set to 0.77 to 3.00.
  • the sectional area of the through-hole 18 can be increased while stiffness and durability of the spacer expander 12 are maintained. Hence, the engine oil that flows in the groove 17 can be smoothly discharged, and deposition of carbon sludge can be suppressed. Such suppression of the deposition of carbon sludge can lead to a reduction in an amount of consumed oil.
  • an amount of deposited sludge in Example 1 significantly decreases to 28% of that in the conventional example.
  • an amount of deposited sludge in the comparative example adopting the grooved configuration 1 decreases to 61% of that in the conventional example, comparing the comparative example with the examples, an amount of deposited sludge in each example further decreases by about 30% or more with respect to that in the comparative example.
  • the combined oil ring according to each example can be considered to have optimal dimensions and shape.
  • the sectional shape of the groove 17 is a V shape.
  • the sectional shape of the groove 17 is not limited thereto, and may be, for example, an R shape in section. As is apparent from contents of "What is claimed is”, modes to which such change or improvement as described above is given can also be included in a technical scope of the present invention.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Claims (5)

  1. Kombinierter Ölring (10) zum Montiert-Sein in einer Ölringnut (3) eines Kolbens (2), aufweisend:
    ein Paar aus einer oberen und einer untereren plattenartigen kreisförmigen Seitenleiste (11),
    einen Abstandhalter (12), der zwischen dem Paar aus der oberen und der unterer Seitenleiste (11) angeordnet ist,
    wobei der Abstandhalter (12) aufweist:
    eine große Anzahl an oberen Teilen (13) und an unteren Teilen (14), welche alternierend in einer Umfangsrichtung angeordnet sind, so dass sie einen Abstand in einer Axialrichtung und in der Umfangsrichtung haben,
    Kuppelteile (15), die jeweils die benachbarten oberen Teile (13) und unteren Teile (14) kuppeln, und
    Nasenteile (16), von denen jedes so geformt ist, dass es an einem inneren Umfangsendabschnitt von jedem der oberen Teile (13) und der unteren Teile (14) vorsteht, und dazu dient, die Seitenleisten (11) zu drücken, wobei
    zumindest eine von einer oberen Fläche (13a) von jedem oberen Teil (13) und einer unteren Fläche von jedem unteren Teil (14) eine Nut (17) aufweist, die daran gebildet ist,
    jedes Nasenteil (16) eine Durchgangsöffnung (18) aufweist, die darin gebildet ist und mit welcher die Nut (17) in Verbindung steht, wobei der kombinierte Ölring (10) dadurch gekennzeichnet ist, dass
    die Durchgangsöffnung (18) so gebildet ist, dass eine Distanz A entlang der Axialrichtung zwischen einer von einer oberen Fläche (16a) und einer unteren Fläche (16b) von jedem Nasenteil (16) an einem höchsten Abschnitt davon und einem tiefsten Abschnitt der Nut (17) gleich oder größer 0,22 mm ist,
    eine Plattendicke T des Abstandhalters (12) auf 0,17 bis 0,28 mm eingestellt ist und
    ein Verhältnis A/T von der Distanz entlang der Axialrichtung zwischen einer von der oberen Fläche (16a) und der unteren Fläche (16b) von jedem Nasenteil (16) an dem höchsten Abschnitt davon und dem tiefsten Abschnitt der Nut (17) zu der Plattendicke des Abstandhalters 0,77 bis 3,00 beträgt.
  2. Kombinierter Ölring (10) gemäß Anspruch 1, wobei eine Schnittfläche der Durchgangsöffnung (18) entlang der Axialrichtung so eingestellt ist, dass sie gleich oder größer 0,10 mm2 ist.
  3. Kombinierter Ölring (10) gemäß Anspruch 1 oder 2, wobei
    der Abstandhalter (12) einen Seitenleiste-Stützteil (19) aufweist, der in einem äußeren Umfangsendendabschnitt von jedem von den oberen Teilen (13) und den unteren Teilen (14) so gebildet ist, dass er eine Stufe höher ist als die Nut (17), und
    ein Abstand B entlang der Axialrichtung zwischen dem Seitenleiste-Stützteil (19) und einem Nutrandteil (17a) der Nut (17) auf 0,04 bis 0,20 mm eingestellt ist.
  4. Kombinierter Ölring (10) gemäß einem der Ansprüche 1 bis 3, wobei
    die Nut (17) entlang einer Radialrichtung gebildet ist.
  5. Kombinierter Ölring (10) gemäß einem der Ansprüche 3 bis 4, wobei der Seitenleiste-Stützteil (19) eine Öffnung (20) aufweist, die darin gebildet ist und mit der Nut (17) in Verbindung steht, und
    eine Schnittfläche der Öffnung (20) entlang der Axialrichtung kleiner ist als eine Schnittfläche der Durchgangsöffnung (18) entlang der Axialrichtung.
EP13181284.4A 2012-08-30 2013-08-22 Kombinierter Schmierring Revoked EP2703695B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2012190201 2012-08-30
JP2013067590 2013-03-27
JP2013154699A JP2014209018A (ja) 2012-08-30 2013-07-25 組合せオイルリング

Publications (2)

Publication Number Publication Date
EP2703695A1 EP2703695A1 (de) 2014-03-05
EP2703695B1 true EP2703695B1 (de) 2015-09-16

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ID=49033865

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13181284.4A Revoked EP2703695B1 (de) 2012-08-30 2013-08-22 Kombinierter Schmierring

Country Status (4)

Country Link
US (1) US9528606B2 (de)
EP (1) EP2703695B1 (de)
JP (1) JP2014209018A (de)
CN (1) CN103670777B (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017108683A1 (de) 2017-04-24 2018-10-25 Scherdel Innotec Forschungs- Und Entwicklungs-Gmbh Ölabstreifring-Feder für einen Ölabstreifring und Ölabstreifring
EP3492782A1 (de) 2017-12-01 2019-06-05 Scherdel Innotec Forschungs- Und Entwicklungs GmbH Ölabstreifring-feder für einen ölabstreifring und ölabstreifring
DE102018114113A1 (de) 2018-06-13 2019-12-19 Scherdel Innotec Forschungs- Und Entwicklungs-Gmbh Ölabstreifring und Zylinderkolben mit einer Ölringnut und einem Ölabstreifring

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JP5970239B2 (ja) * 2012-05-28 2016-08-17 株式会社リケン 組合せオイルコントロールリング
JP6122901B2 (ja) * 2014-07-31 2017-04-26 日本ピストンリング株式会社 組合せオイルリング
EP3279525B1 (de) * 2015-03-31 2022-09-07 Nippon Piston Ring Co., Ltd. Kombinierter schmierring
JP6013548B1 (ja) * 2015-04-09 2016-10-25 株式会社リケン 組合せオイルコントロールリング
JP6518493B2 (ja) * 2015-04-09 2019-05-22 株式会社リケン 組合せオイルコントロールリング
US10571024B2 (en) 2017-07-05 2020-02-25 Tpr Co., Ltd. Combination oil ring
CN109844379B (zh) * 2017-09-29 2020-05-15 帝伯爱尔株式会社 刮片环、组合油环以及刮片环的制造方法
JP6389970B1 (ja) * 2018-01-16 2018-09-12 Ｔｐｒ株式会社 組合せオイルリング

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US2904377A (en) 1957-05-21 1959-09-15 Muskegon Piston Ring Co Inc Spacer and expander for piston rings
US5195758A (en) 1991-11-19 1993-03-23 Hastings Manufacturing Company Three-piece oil control ring assembly
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JP4633639B2 (ja) * 2006-01-31 2011-02-16 日本ピストンリング株式会社 ３ピースオイルリング及び３ピースオイルリングとピストンとの組合せ
JP5342711B2 (ja) * 2011-03-31 2013-11-13 株式会社リケン 組合せオイルリング
JP5587285B2 (ja) * 2011-12-21 2014-09-10 Ｔｐｒ株式会社 組合せオイルリング
JP5970239B2 (ja) * 2012-05-28 2016-08-17 株式会社リケン 組合せオイルコントロールリング
JP6239964B2 (ja) * 2013-12-18 2017-11-29 株式会社リケン 組合せオイルコントロールリング

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Publication number Priority date Publication date Assignee Title
US2904377A (en) 1957-05-21 1959-09-15 Muskegon Piston Ring Co Inc Spacer and expander for piston rings
US5195758A (en) 1991-11-19 1993-03-23 Hastings Manufacturing Company Three-piece oil control ring assembly
US20110221141A1 (en) 2010-03-10 2011-09-15 Teikoku Piston Ring Co., Ltd. Combination oil ring

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017108683A1 (de) 2017-04-24 2018-10-25 Scherdel Innotec Forschungs- Und Entwicklungs-Gmbh Ölabstreifring-Feder für einen Ölabstreifring und Ölabstreifring
WO2018197450A1 (de) 2017-04-24 2018-11-01 Scherdel Innotec Forschungs- Und Entwicklungs-Gmbh Ölabstreifring-feder für einen ölabstreifring und ölabstreifring
EP3492782A1 (de) 2017-12-01 2019-06-05 Scherdel Innotec Forschungs- Und Entwicklungs GmbH Ölabstreifring-feder für einen ölabstreifring und ölabstreifring
DE102018114113A1 (de) 2018-06-13 2019-12-19 Scherdel Innotec Forschungs- Und Entwicklungs-Gmbh Ölabstreifring und Zylinderkolben mit einer Ölringnut und einem Ölabstreifring

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EP2703695A1 (de) 2014-03-05
CN103670777A (zh) 2014-03-26
US9528606B2 (en) 2016-12-27
US20140062030A1 (en) 2014-03-06
JP2014209018A (ja) 2014-11-06
CN103670777B (zh) 2016-04-27

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